EP0300843A1 - Gear pinion brake device of a motor vehicle gearbox - Google Patents

Gear pinion brake device of a motor vehicle gearbox Download PDF

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Publication number
EP0300843A1
EP0300843A1 EP88401455A EP88401455A EP0300843A1 EP 0300843 A1 EP0300843 A1 EP 0300843A1 EP 88401455 A EP88401455 A EP 88401455A EP 88401455 A EP88401455 A EP 88401455A EP 0300843 A1 EP0300843 A1 EP 0300843A1
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EP
European Patent Office
Prior art keywords
slide
gear
synchronized
finger
passage
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP88401455A
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German (de)
French (fr)
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EP0300843B1 (en
Inventor
Jean-Claude Raynaud
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Automobiles Peugeot SA
Automobiles Citroen SA
Original Assignee
Automobiles Peugeot SA
Automobiles Citroen SA
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Publication date
Application filed by Automobiles Peugeot SA, Automobiles Citroen SA filed Critical Automobiles Peugeot SA
Publication of EP0300843A1 publication Critical patent/EP0300843A1/en
Application granted granted Critical
Publication of EP0300843B1 publication Critical patent/EP0300843B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/20—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear
    • F16H3/38—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear with synchro-meshing
    • F16H3/385—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear with synchro-meshing with braking means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/08—Multiple final output mechanisms being moved by a single common final actuating mechanism
    • F16H63/20—Multiple final output mechanisms being moved by a single common final actuating mechanism with preselection and subsequent movement of each final output mechanism by movement of the final actuating mechanism in two different ways, e.g. guided by a shift gate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H63/302—Final output mechanisms for reversing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/08—Multiple final output mechanisms being moved by a single common final actuating mechanism
    • F16H63/20—Multiple final output mechanisms being moved by a single common final actuating mechanism with preselection and subsequent movement of each final output mechanism by movement of the final actuating mechanism in two different ways, e.g. guided by a shift gate
    • F16H2063/208—Multiple final output mechanisms being moved by a single common final actuating mechanism with preselection and subsequent movement of each final output mechanism by movement of the final actuating mechanism in two different ways, e.g. guided by a shift gate using two or more selecting fingers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H2063/3086—Shift head arrangements, e.g. forms or arrangements of shift heads for preselection or shifting

Definitions

  • the present invention relates to a device for braking gears of a gearbox of a motor vehicle.
  • the gearbox gears have a rotational inertia which, when engaging in the stop of an unsynchronized gear such as for example reverse, causes a very unpleasant cracking for the user of the vehicle equipped with such a gearbox.
  • the present invention provides a gearbox braking device comprising at least one gear fitted with a friction synchronizer actuated by a first slide whose axial displacement in the direction of the passage, is controlled by a finger previously engaged in a control stick secured to the slide, from a neutral position, by a selection movement in a direction perpendicular to the axis of movement of the slide, and an unsynchronized ratio, the passage is controlled by axial displacement of a second slide, parallel to the first slide and in the direction opposite to the direction of passage of the latter, by means of a finger previously brought opposite an element of drive, integral with the second slide, by a selection movement of the same direction and of amplitude equal to or greater than that of the selection movement of the synchronized gear, l e device also comprising means causing part of said axial displacement of the first slide, during the movement for selecting the non-synchronized report, so as to drive the synchronizer prior to the passage of the non-synchronized report, characterized in that said
  • each of the two slides is equipped with a neutral billing device, the billing device associated with the second slide being tared elastically so axially immobilizing the latter relative to the gearbox casing when the control finger of the synchronized gear cooperates with the ramp.
  • the two slides are coaxial and axially movable relative to the other with a maximum stroke substantially equal to said part of the axial displacement of the first slide, the stock comprising a first integral part of the first slider and on which the ramp is formed, and a second part integral with the second slider, disposed opposite the first part, and which constitutes the drive element, the two synchronized gear control fingers and not synchronized being constituted by a single control finger.
  • control finger for the synchronized gear and the control finger for the non-synchronized gear are two separate fingers linked in translation and in rotation to a control shaft mounted to slide and rotate in the gearbox casing, the stock having a projection, disposed opposite the ramp, with which the control finger of the synchronized gear cooperates, at the end of the shift of the non-synchronized report, so as to bring the first slide back into its neutral position.
  • the non-synchronized gear is reverse gear and the synchronized gear is the highest-ranking forward gear.
  • FIG. 1 An internal control device of a gearbox which one can see a part of the housing 10.
  • the gearbox shown is a gearbox with five forward gears and a reverse gear and three axes of passage 12, 14 and 16.
  • the three passage axes 12, 14 and 16 are slidably mounted and parallel to each other inside the housing 10.
  • the three passage axes 12, 14 and 16 which are shown in neutral point in the same vertical plane perpendicular to their direction of axial movement, one or two cylindrical millings, the central axis 14 further comprising at the right of these millings a snowman 18 sliding in a bore and which comes into play only during the displacement of an external passage axis 12 or 16.
  • the lower passage axis 16 controls, under the action of a control finger 20 which cooperates with a passage stock 22, the passage of the first or second forward gear depending on whether the axis is moved axially, respectively to the right or to the left when considering FIG. 1.
  • the central passage axis 14 controls, under the action of the finger 20 which cooperates with a control stock 24, the passage of the third or fourth forward gear according to that the control axis 14 is moved axially to the right or respectively to the left.
  • the upper passage axis 12 controls, in a manner which will be described later, the passage of the fifth forward gear, or the reverse gear depending on whether the passage axis 12 is moved axially to the right or respectively to the left by the control finger 20.
  • the fifth forward gear which in this gearbox is the highest-ranking forward gear, is equipped with a friction synchronizer (not shown) which is actuated by a fork 26, actuating the synchronizer and for the passage of the fifth gear, which is fixed to the left free end of the first passage axis 12 by means of a screw 28 which immobilizes it in translation and in rotation.
  • the fork 26 is actuated by means of a slide 30 mounted on the first passage axis 12 by means of a screw 32 which immobilizes it in translation and in rotation on the passage axis 12.
  • L ' cylindrical passage axis 12, the fork 26, and the slide 30 thus form a structural unit which can move axially relative to the gearbox casing 10.
  • a second slide 34 is mounted on the passage axis 12 with respect to which it can slide axially.
  • the second slide 34 is equipped with a neutral point billing device 36, resiliently calibrated by a spring 38, which makes it possible to immobilize the second slide 34 axially relative to the casing 10 of the gearbox, in particular in its position of neutral point shown in Figure 1.
  • the second slide 34 is provided with an axial extension 40 extending to the right, considering Figure 1, and whose end is folded at 90 ° so as to constitute a drive element 42 of the second slide 34 which extends in a plane substantially perpendicular to the axis of movement of the slide 34.
  • the axial extension 40 is formed by a bar welded to the substantially cylindrical external surface of the second slide 34.
  • the axial extension 40 of the slide 34 and its folded end 42 slide on a first vertical guide surface 44, considering FIGS. 2 and 3, as well as on a horizontal surface 46 which are both formed in the first slide 30 of which they delimit a notched portion at a right angle 48.
  • the notched portion 48 is also delimited axially to the right by a transverse abutment wall 50 which cooperates with the lateral face opposite screw 52 of the drive end 42 of the extension 40 of the second slide 34.
  • the guide surfaces 44 and 46 in cooperation with the extension 40 of the second slide 34, immobilizes the latter in rotation relative to the axis of passage 12.
  • the drive element 42 constitutes the first part of a two-part slide stock, the second part of which is formed by an extension 54 made integrally with the slide 30.
  • l drive element 42 and the second part 54 of the stick are arranged opposite one another so as to form a stick inside which is capable of engaging the finger command 20.
  • the control finger 20 which, in this embodiment, is a single control finger for the selection and shifting from the fifth forward or reverse gear, is connected to the gear change lever (not shown).
  • the control finger 20 can move in a first direction, extending in a plane perpendicular to the passage axes 12, 14 and 16, called the selection direction. It performs selection movements, vertically upwards or downwards by considering FIGS. 1 to 4, in order to engage in one of the sticks 22, 24 or in the third stick formed from the two parts 42 and 54, according to the group of two reports, among which is the report that you want to select for its subsequent passage.
  • the control finger 20 is shown in its so-called neutral position in which it is engaged in the stock 24 for passing the third and fourth forward gears.
  • the control finger 20 can move in a second direction, perpendicular to the selection direction, in two opposite directions of passage corresponding to the passage of one or the other of the two reports associated with the stock in which it was previously engaged.
  • the gearbox shown in FIGS. 1 to 5 comprises a pinion braking device comprising means causing part of the axial displacement of the first slider 30, during the movement for selecting the non-synchronized reverse gear ratio, so as to drive the synchronizer of the fifth forward gear prior to the passage of the reverse gear.
  • These means consist of an inclined ramp 56 formed on the first part 54, soli Daire of the first slide 30, of the butt in two parts associated with the axis of upper passage 12.
  • the ramp 56 is oriented and dimensioned so that, when the two parts 42 and 54 of the butt are in abutment one against the other, the average distance "d" separating the ramp 56 from the drive element 42 is less than the axial width "1" of the control finger 20.
  • the two slides 30 and 34, and therefore the two parts 42 and 54 of the stick are resiliently biased, in a direction corresponding to the bringing together of the two parts of the stick and to the cooperation of the abutment surfaces facing each other 50 and 52, by means of a compression spring 58.
  • the compression spring 58 is disposed between a shoulder 60 of the fork 26 and a shoulder facing 62 of the second slide 34.
  • the spring 58 is capable of be compressed axially between the shoulders 60 and 62, until its turns become contiguous, with a maximum stroke "x" which determines the maximum relative travel between the first slide 30 and the second slide 34 and therefore the maximum spacing possible between the drive element 42 and the first part 54 of the stick.
  • this clearance and this maximum spacing are provided by bringing the faces into contact with respective end portions of the slides 30 and 34, the turns of the spring 58 then no longer being contiguous.
  • the elastic calibration of the neutral point billing 36 of the second slide 34 has a sufficiently high value so as to immobilize the second slide 34 axially relative to the casing 10 when the control finger 20 cooperates with the ramp 56, and allowing the drive element 42 to absorb the force of reaction to the thrust P exerted on the control finger 20.
  • control finger 20 At the end of its selection movement, the control finger 20 is fully engaged inside the stick in two parts of which it has caused an axial spacing of a value x equal to the maximum possible value of relative travel between the two sliders 30 and 34, the spring 58 then being compressed by this value x and its turns being contiguous.
  • the reverse gear is shifted after the selection movement which comes to be described, by causing an axial displacement of the second slide 34 to the left, by means of the control finger 20.
  • an actuation of the control finger by the gear shift lever to the left has the effect of causing the drive of the second slide 34.
  • the displacement of the second slide 34, at the 'against the elastic force exerted by the billing device 36 causes, via the spring 58 whose turns are contiguous, or alternatively, via the above faces opposite, the drive of the fork 26 and thus of the first slide 30 relative to the casing 10 of the gearbox.
  • the displacement to the left of the second slide 30, that is to say in the direction opposite to the direction of passage of the fifth forward gear, causes the rotation of a fork 64 for shifting the reverse gear pivotally mounted around 'an axis 66 of the casing 10 and one end 68 of which is received in a corresponding notch 70 of the first slide 30.
  • the displacement of the latter also causes the synchronizer of the fifth gear to disengage, which makes the engagement of the teeth free reverse gear.
  • the right side stock, integral with a first slide 130 allows the selection and the passage of the fifth forward gear.
  • it comprises a vertical branch 154 with which a first control finger 120 of the fifth synchronized forward gear is capable of cooperating.
  • the control finger 120 is immobilized in rotation and in translation relative to a control shaft 70 for the selection and shifting of gears, mounted sliding and rotatable in the casing of the gearbox.
  • a second control finger 72 is mounted on the control shaft 70 relative to which it is also immobilized in translation and in rotation.
  • the lower end 74 of the second control finger 72 is capable of cooperating with a drive element 142 formed by a vertical branch of a second slide 134 to which the gear of the non-synchronized reverse gear is connected.
  • the passage of the fifth synchronized forward gear is effected by sliding the first slider 130 parallel to its direction of passage, that is to say in a direction perpendicular to the selection direction which is parallel to the axis of command 70.
  • the shift from the reverse gear is effected by causing the second slide 134 to move parallel to the direction of passage of the fifth forward gear but in the opposite direction to the direction of shift of the latter gear.
  • the butt portion 154 of the first slide 130 comprises a ramp 156 with which the first control finger 120 of the fifth synchronized forward gear cooperates when it is moved, in the selection direction, towards the right considering the figures, until it is fully engaged inside the butt of the first slide 130 and as shown in Figure 7c. Since the second control finger 72 is linked in translation to the first control finger 120, the movement of the latter to the right causes a displacement of the second control finger 72 so that the latter is brought simultaneously opposite the drive element 142 of the second slide 134 as can be seen in Figures 7b and 7c.
  • the engagement of the first control finger 120 inside the stock of the first slide 130 causes an upward movement, considering FIGS. 7a to 7c, of the stock portion 154 and therefore of the first slide 130 of a stroke "x" whose value is determined by the profile and orientation of the ramp 156.
  • the displacement of the first slide 130 of a stroke "x" equal to part of its axial displacement in the direction of passage of the fifth speed has the effect of causing the synchronizer fitted to the fifth forward gear and therefore to cause the gearbox input gear to brake.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gear-Shifting Mechanisms (AREA)
  • Mechanical Operated Clutches (AREA)
  • Structure Of Transmissions (AREA)

Abstract

1. Gear-pinion brake device of a motor-vehicle gearbox, comprising at least one gear (5th) equipped with a friction synchroniser actuated by a first slide (30, 130) the axial movement of which in the changing direction is controlled by a finger (20, 120) previously engaged in a control crosshead (42-54-142-154) fixed to the slide, from a dead-centre position as a result of a selecting movement in a direction perpendicular to the axis of movement of the slide, and a non-synchronised gear (reverse), the changing of which is controlled by the axial movement of a second slide (34, 134) in parallel with the first slide and in the opposite direction to the changing direction of the latter, by means of a finger (20, 72) previously brought opposite a driving element (42, 142) fixed to the second slide, as a result of a selecting movement in the same direction as and of an amount equal to or greater than those of the selecting movement of the synchronised gear, the device also comprising means causing a part (x) of the said axial movement of the first slide during the selecting movement of the non-synchronised gear, so as to drive the synchroniser before the changing of the non-synchronised gear, characterized in that the said means comprise a ramp (56, 156) which is formed on a part (54, 154) of the control crosshead of the first slide and with which the control finger (20, 120) of the synchronised gear interacts when the control finger of the non-synchronised gear is brought opposite the driving element.

Description

La présente invention a pour objet un dispositif de freinage de pignons d'une boîte de vitesses de véhicule automobile.The present invention relates to a device for braking gears of a gearbox of a motor vehicle.

Les engrenages des boîtes de vitesses possèdent une inertie en rotation qui, lors de l'engagement à l'arrêt d'un rapport non synchronisé tel que par exemple la marche arrière, entraîne un craquement très désagréable pour l'utilisateur du véhicule équipé d'une telle boîte de vitesses.The gearbox gears have a rotational inertia which, when engaging in the stop of an unsynchronized gear such as for example reverse, causes a very unpleasant cracking for the user of the vehicle equipped with such a gearbox.

Différentes solutions ont été proposées pour remédier à cet inconvénient. Il est possible d'équiper le rapport de marche arrière d'un synchroniseur à friction qui agit directement sur le pignon de marche arrière pendant la course de passage de la marche arrière. Etant donné que le couple de freinage nécessaire pour arrêter la rotation des engrenages d'une boîte de vitesses est proportionnel au cube du rapport de multiplication et au diamètre du synchroni­seur, le freinage au moyen d'un synchroniseur de petit diamètre équipant un rapport court de la boîte de vitesses, tel que par exemple la marche arrière, est particulièrement défavorable.Different solutions have been proposed to remedy this drawback. It is possible to equip the reverse gear with a friction synchronizer which acts directly on the reverse gear during the reverse gear shift. Since the braking torque required to stop the rotation of the gears of a gearbox is proportional to the cube of the multiplication ratio and to the diameter of the synchronizer, braking by means of a small diameter synchronizer fitted with a short ratio of the gearbox, such as for example reverse gear, is particularly unfavorable.

On a également proposé de ralentir les pignons en utilisant un des synchroniseurs de la boîte de vitesses, tel que par exemple celui équipant le quatrième rapport, en l'entraînant partiellement du­rant le début de la course de sélection et de passage de la marche arrière. Une telle solution est notamment décrite dans le brevet US n° 4.510.818. On constate toutefois que dans un tel système, plusieurs pièces frottantes interviennent de façon complexe et peu fiable, et le dégagement du synchroniseur est réalisé de manière imprécise, élastiquement et non positive­ment, lors de l'engagement de la denture de marche arrière, ce qui se traduit par une dureté de commande et des craquements lors du passage de ce rapport.It has also been proposed to slow down the pinions by using one of the gearbox synchronizers, such as for example the one fitted to the fourth gear, by partially driving it during the start of the selection race and shifting from reverse gear. Such a solution is described in particular in US Patent No. 4,510,818. However, it can be seen that in such a system, several rubbing parts are involved in a complex and unreliable manner, and the synchronizer is released imprecisely, elastically and not positively, when the gears are engaged. rear, which results in a hardness of control and creaking when passing this report.

Afin de remédier aux inconvénients des solutions antérieures, la présente invention propose un dispositif de freinage de pignons d'une boîte de vitesses comportant au moins un rapport équipé d'un synchroniseur à friction actionné par un premier coulisseau dont le déplacement axial, dans le sens du passage, est commandé par un doigt préalablement en­gagé dans une crosse de commande solidaire du cou­lisseau, depuis une position de point mort, par un mouvement de sélection selon une direction perpendi­culaire à l'axe de déplacement du coulisseau, et un rapport non synchronisé dont le passage est commandé par déplacement axial d'un second coulisseau, paral­lèlement au premier coulisseau et dans le sens opposé au sens de passage de ce dernier, au moyen d'un doigt préalablement amené en vis-à-vis d'un élément d'en­traînement, solidaire du second coulisseau, par un mouvement de sélection de même sens et d'amplitude égale ou supérieure à ceux du mouvement de sélection du rapport synchronisé, le dispositif comportant éga­lement des moyens provoquant une partie dudit déplace­ment axial du premier coulisseau, lors du mouvement de sélection du rapport non synchronisé, de façon à en­traîner le synchroniseur préalablement au passage du rapport non synchronisé, caractérisé en ce que lesdits moyens comportent une rampe, formée sur une partie de la crosse de commande du premier coulisseau avec laquelle coopère le doigt de commande du rapport synchronisé lorsque le doigt de commande du rapport non synchronisé est amené en vis-à-vis de l'élément d'entraînement.In order to overcome the drawbacks of previous solutions, the present invention provides a gearbox braking device comprising at least one gear fitted with a friction synchronizer actuated by a first slide whose axial displacement in the direction of the passage, is controlled by a finger previously engaged in a control stick secured to the slide, from a neutral position, by a selection movement in a direction perpendicular to the axis of movement of the slide, and an unsynchronized ratio, the passage is controlled by axial displacement of a second slide, parallel to the first slide and in the direction opposite to the direction of passage of the latter, by means of a finger previously brought opposite an element of drive, integral with the second slide, by a selection movement of the same direction and of amplitude equal to or greater than that of the selection movement of the synchronized gear, l e device also comprising means causing part of said axial displacement of the first slide, during the movement for selecting the non-synchronized report, so as to drive the synchronizer prior to the passage of the non-synchronized report, characterized in that said means comprise a ramp, formed on a part of the control stick of the first slide with which the control finger for the synchronized gear cooperates when the control finger for the non-synchronized gear is brought opposite the drive element.

Selon une autre caractéristique de l'inven­ tion, et notamment dans le cas où la boîte de vitesses est une boîte possédant trois axes de passage, chacun des deux coulisseaux est équipé d'un dispositif de billage de point mort, le dispositif de billage associé au second coulisseau étant taré élastiquement de manière à immobiliser axialement ce dernier par rapport au carter de la boîte de vitesses lorsque le doigt de commande du rapport synchronisé coopère avec la rampe.According to another characteristic of the invention tion, and in particular in the case where the gearbox is a gearbox having three axes of passage, each of the two slides is equipped with a neutral billing device, the billing device associated with the second slide being tared elastically so axially immobilizing the latter relative to the gearbox casing when the control finger of the synchronized gear cooperates with the ramp.

Selon un mode de réalisation particulière­ment avantageux de l'invention, les deux coulisseaux sont coaxiaux et mobiles axialement par rapport à l'autre d'une course maximale sensiblement égale à ladite partie du déplacement axial du premier cou­lisseau, la crosse comprenant une première partie solidaire du premier coulisseau et sur laquelle est formée la rampe, et une seconde partie solidaire du second coulisseau, disposée en vis-à-vis de la pre­mière partie, et que constitue l'élément d'entraîne­ment, les deux doigts de commande des rapports syn­chronisé et non synchronisé étant constitués par un doigt de commande unique.According to a particularly advantageous embodiment of the invention, the two slides are coaxial and axially movable relative to the other with a maximum stroke substantially equal to said part of the axial displacement of the first slide, the stock comprising a first integral part of the first slider and on which the ramp is formed, and a second part integral with the second slider, disposed opposite the first part, and which constitutes the drive element, the two synchronized gear control fingers and not synchronized being constituted by a single control finger.

Selon un autre mode de réalisation de l'invention, et dans le cas d'une boîte de vitesses comportant quatre couloirs de passage parallèles, le doigt de commande du rapport synchronisé et le doigt de commande du rapport non synchronisé sont deux doigts distincts liés en translation et en rotation à un arbre de commande monté coulissant et rotatif dans le carter de la boîte de vitesses, la crosse compor­tant une saillie, disposée en vis-à-vis de la rampe, avec laquelle coopère le doigt de commande du rapport synchronisé, en fin de passage du rapport non synchro­nisé, de façon à ramener le premier coulisseau dans sa position de point mort.According to another embodiment of the invention, and in the case of a gearbox comprising four parallel passage lanes, the control finger for the synchronized gear and the control finger for the non-synchronized gear are two separate fingers linked in translation and in rotation to a control shaft mounted to slide and rotate in the gearbox casing, the stock having a projection, disposed opposite the ramp, with which the control finger of the synchronized gear cooperates, at the end of the shift of the non-synchronized report, so as to bring the first slide back into its neutral position.

Selon l'invention le rapport non synchronisé est la marche arrière et le rapport synchronisé est le rapport de marche avant de rang le plus élevé.According to the invention, the non-synchronized gear is reverse gear and the synchronized gear is the highest-ranking forward gear.

D'autres caractéristiques et avantages de l'invention apparaîtront à la lecture de la descrip­tion détaillée qui va suivre pour la compréhension de laquelle on se reportera aux dessins annexés dans lesquels :

  • - La figure 1 est une vue simplifiée, en coupe partielle, d'une boîte de vitesses à cinq rapports de marche avant et un rapport de marche arrière, à trois axes de passage, équipée d'un dispositif de freinage de pignons réalisé conformément aux enseignements de l'invention;
  • - la figure 2 est une vue en coupe selon la ligne 2-2 de la figure 1 ;
  • - la figure 3 est une vue partielle en perspective selon la flèche F de la figure 2, le doigt de commande étant engagé dans la crosse du coulisseau associé à la marche arrière et au cinquième rapport de marche avant ;
  • - la figure 4 est une vue partielle selon la flèche F de la figure 2, le doigt de commande étant engagé dans la crosse associée aux troisième et qua­trième rapports de marche avant ;
  • - les figures 5a et 5b sont des vues en coupe partielle selon la ligne 5-5 de la figure 4 ;
  • - la figure 6 est une vue schématique en perspective d'un dispositif de freinage de pignons selon l'invention utilisé dans une boîte de vitesses à quatre couloirs de passage, le levier de changement de vitesses étant en position de point mort entre les troisième et quatrième rapports ;
  • - la figure 7a est une vue en coupe selon la ligne 7-7 de la figure 6 ;
  • - la figure 7b est une vue similaire à celle de la figure 7a lors du début du mouvement de sélec­tion du rapport non synchronisé ; et
  • - la figure 7c est une vue similaire à celle de la figure 7a à l'issue du mouvement de sélection du rapport non synchronisé.
Other characteristics and advantages of the invention will appear on reading the detailed description which follows for the understanding of which reference will be made to the appended drawings in which:
  • - Figure 1 is a simplified view, in partial section, of a gearbox with five forward gears and a reverse gear, with three shift axes, equipped with a pinion braking device produced in accordance with lessons of the invention;
  • - Figure 2 is a sectional view along line 2-2 of Figure 1;
  • - Figure 3 is a partial perspective view along arrow F of Figure 2, the control finger being engaged in the butt of the slide associated with reverse and the fifth forward gear ratio;
  • - Figure 4 is a partial view along arrow F of Figure 2, the control finger being engaged in the butt associated with the third and fourth forward gear;
  • - Figures 5a and 5b are partial sectional views along line 5-5 of Figure 4;
  • FIG. 6 is a schematic perspective view of a pinion braking device according to the invention used in a gearbox with four shift lanes, the gear shift lever being in the neutral position between the third and fourth gear;
  • - Figure 7a is a sectional view along line 7-7 of Figure 6;
  • - Figure 7b is a view similar to that of Figure 7a at the start of the gear selection movement unsynchronized; and
  • - Figure 7c is a view similar to that of Figure 7a at the end of the gear selection movement not synchronized.

On a représenté à la figure 1 un dispositif de commande interne d'une boîte de vitesses dont on peut voir une partie du carter 10. La boîte de vites­ses représentée est une boîte de vitesses à cinq rapports de marche avant et un rapport de marche arrière et à trois axes de passage 12, 14 et 16.There is shown in Figure 1 an internal control device of a gearbox which one can see a part of the housing 10. The gearbox shown is a gearbox with five forward gears and a reverse gear and three axes of passage 12, 14 and 16.

Les trois axes de passage 12, 14 et 16 sont montés coulissants et parallèles entre eux à l'inté­rieur du carter 10. Les trois axes de passage 12, 14 et 16 qui sont représentés au point mort portent, dans un même plan vertical perpendiculaire à leur direction de déplacement axial, un ou deux fraisages cylindri­ques, l'axe central 14 comportant en outre au droit de ces fraisages un bonhomme 18 coulissant dans un perça­ge et qui n'entre en jeu que lors du déplacement d'un axe de passage extérieur 12 ou 16.The three passage axes 12, 14 and 16 are slidably mounted and parallel to each other inside the housing 10. The three passage axes 12, 14 and 16 which are shown in neutral point in the same vertical plane perpendicular to their direction of axial movement, one or two cylindrical millings, the central axis 14 further comprising at the right of these millings a snowman 18 sliding in a bore and which comes into play only during the displacement of an external passage axis 12 or 16.

L'axe de passage inférieur 16 commande, sous l'action d'un doigt de commande 20 qui coopère avec une crosse de passage 22, le passage du premier ou du second rapport de marche avant selon que l'axe est déplacé axialement, respectivement vers la droite ou vers la gauche en considérant la figure 1. L'axe de passage central 14 commande, sous l'action du doigt 20 qui coopère avec une crosse de commande 24, le passage du troisième ou du quatrième rapport de marche avant selon que l'axe de commande 14 est déplacé axialement vers la droite ou respectivement vers la gauche. L'axe de passage supérieur 12 commande, d'une façon qui sera décrite plus avant, le passage du cinquième rapport de marche avant, ou du rapport de marche arrière selon que l'axe de passage 12 est déplacé axialement vers la droite ou respectivement vers la gauche par le doigt de commande 20.The lower passage axis 16 controls, under the action of a control finger 20 which cooperates with a passage stock 22, the passage of the first or second forward gear depending on whether the axis is moved axially, respectively to the right or to the left when considering FIG. 1. The central passage axis 14 controls, under the action of the finger 20 which cooperates with a control stock 24, the passage of the third or fourth forward gear according to that the control axis 14 is moved axially to the right or respectively to the left. The upper passage axis 12 controls, in a manner which will be described later, the passage of the fifth forward gear, or the reverse gear depending on whether the passage axis 12 is moved axially to the right or respectively to the left by the control finger 20.

Le cinquième rapport de marche avant, qui dans cette boîte de vitesses est le rapport de marche avant de rang le plus élevé, est équipé d'un synchro­niseur à friction (non représenté) qui est actionné par une fourchette 26, d'actionnement du synchroniseur et de passage du cinquième rapport, qui est fixée à l'extrémité libre gauche du premier axe de passage 12 au moyen d'une vis 28 qui l'immobilise en translation et en rotation. L'actionnement de la fourchette 26 est effectué au moyen d'un coulisseau 30 monté sur le pre­mier axe de passage 12 au moyen d'une vis 32 qui l'immobilise en translation et en rotation sur l'axe de passage 12. L'axe de passage cylindrique 12, la fourchette 26, et le coulisseau 30 forment ainsi une unité structurelle qui peut se déplacer axialement par rapport au carter de la boîte de vitesses 10.The fifth forward gear, which in this gearbox is the highest-ranking forward gear, is equipped with a friction synchronizer (not shown) which is actuated by a fork 26, actuating the synchronizer and for the passage of the fifth gear, which is fixed to the left free end of the first passage axis 12 by means of a screw 28 which immobilizes it in translation and in rotation. The fork 26 is actuated by means of a slide 30 mounted on the first passage axis 12 by means of a screw 32 which immobilizes it in translation and in rotation on the passage axis 12. L ' cylindrical passage axis 12, the fork 26, and the slide 30 thus form a structural unit which can move axially relative to the gearbox casing 10.

Un second coulisseau 34 est monté sur l'axe de passage 12 par rapport auquel il peut coulisser axialement. Le second coulisseau 34 est équipé d'un dispositif de billage de point mort 36, taré élasti­quement par un ressort 38, qui permet d'immobiliser axialement le second coulisseau 34 par rapport au carter 10 de la boîte de vitesses, notamment dans sa position de point mort représentée à la figure 1. Le second coulisseau 34 est muni d'un prolongement axial 40 s'étendant vers la droite, en considérant la figure 1, et dont l'extrémité est repliée à 90° de façon à constituer un élément d'entraînement 42 du second coulisseau 34 qui s'étend dans un plan sensiblement perpendiculaire à l'axe de déplacement du coulisseau 34. Dans le mode de réalisation représenté à la figure 1, le prolongement axial 40 est formé d'un barreau soudé à la surface externe sensiblement cylindrique du second coulisseau 34.A second slide 34 is mounted on the passage axis 12 with respect to which it can slide axially. The second slide 34 is equipped with a neutral point billing device 36, resiliently calibrated by a spring 38, which makes it possible to immobilize the second slide 34 axially relative to the casing 10 of the gearbox, in particular in its position of neutral point shown in Figure 1. The second slide 34 is provided with an axial extension 40 extending to the right, considering Figure 1, and whose end is folded at 90 ° so as to constitute a drive element 42 of the second slide 34 which extends in a plane substantially perpendicular to the axis of movement of the slide 34. In the embodiment shown in FIG. 1, the axial extension 40 is formed by a bar welded to the substantially cylindrical external surface of the second slide 34.

Comme on peut le constater, notamment aux figures 2 et 3, le prolongement axial 40 du coulisseau 34 et son extrémité repliée 42 coulissent sur une pre­mière surface de guidage verticale 44, en considérant les figures 2 et 3, ainsi que sur une surface horizon­tale 46 qui sont toutes les deux formées dans le pre­mier coulisseau 30 dont elles délimitent une portion encochée à angle droit 48. La portion encochée 48 est également délimitée axialement vers la droite par une paroi transversale de butée 50 qui coopère avec la face latérale en vis-à-vis 52 de l'extrémité d'entraî­nement 42 du prolongement 40 du second coulisseau 34. Les surfaces de guidage 44 et 46, en coopération avec le prolongement 40 du second coulisseau 34, immobilise ce dernier en rotation par rapport à l'axe de passage 12.As can be seen, in particular in FIGS. 2 and 3, the axial extension 40 of the slide 34 and its folded end 42 slide on a first vertical guide surface 44, considering FIGS. 2 and 3, as well as on a horizontal surface 46 which are both formed in the first slide 30 of which they delimit a notched portion at a right angle 48. The notched portion 48 is also delimited axially to the right by a transverse abutment wall 50 which cooperates with the lateral face opposite screw 52 of the drive end 42 of the extension 40 of the second slide 34. The guide surfaces 44 and 46, in cooperation with the extension 40 of the second slide 34, immobilizes the latter in rotation relative to the axis of passage 12.

L'élément d'entraînement 42 constitue la première partie d'une crosse de coulisseau en deux parties dont la seconde partie est formée par un prolongement 54 venu de matière avec le coulisseau 30. Comme on peut le constater aux figures 1 à 4, l'élé­ment d'entraînement 42 et la seconde partie 54 de la crosse sont disposés en vis-à-vis l'un de l'autre de manière à former une crosse à l'intérieur de laquelle est susceptible de s'engager le doigt de commande 20.The drive element 42 constitutes the first part of a two-part slide stock, the second part of which is formed by an extension 54 made integrally with the slide 30. As can be seen in FIGS. 1 to 4, l drive element 42 and the second part 54 of the stick are arranged opposite one another so as to form a stick inside which is capable of engaging the finger command 20.

Le doigt de commande 20 qui, dans ce mode de réalisation, est un doigt de commande unique pour la sélection et le passage du cinquième rapport de marche avant ou de la marche arrière, est relié au levier de changement de vitesses (non représenté). Le doigt de commande 20 peut se déplacer selon une première direc­tion, s'étendant dans un plan perpendiculaire aux axes de passage 12, 14 et 16, appelée direction de sélec­tion. Il effectue des mouvements de sélection, verti­calement vers le haut ou vers le bas en considérant les figures 1 à 4, pour venir s'engager dans l'une des crosses 22, 24 ou dans la troisième crosse formée des deux parties 42 et 54, selon le groupe de deux rap­ports parmi lesquels figure le rapport que l'on veut sélectionner en vue de son passage ultérieur. Aux figures 1, 2 et 4, le doigt de commande 20 est représenté dans sa position dite de point mort dans laquelle il est engagé dans la crosse 24 de passage des troisième et quatrième rapports de marche avant.The control finger 20 which, in this embodiment, is a single control finger for the selection and shifting from the fifth forward or reverse gear, is connected to the gear change lever (not shown). The control finger 20 can move in a first direction, extending in a plane perpendicular to the passage axes 12, 14 and 16, called the selection direction. It performs selection movements, vertically upwards or downwards by considering FIGS. 1 to 4, in order to engage in one of the sticks 22, 24 or in the third stick formed from the two parts 42 and 54, according to the group of two reports, among which is the report that you want to select for its subsequent passage. In Figures 1, 2 and 4, the control finger 20 is shown in its so-called neutral position in which it is engaged in the stock 24 for passing the third and fourth forward gears.

Le doigt de commande 20 peut se déplacer selon une seconde direction, perpendiculaire à la direction de sélection, selon deux sens de passage opposés correspondant au passage de l'un ou de l'autre des deux rapports associés à la crosse dans laquelle il a été préalablement engagé.The control finger 20 can move in a second direction, perpendicular to the selection direction, in two opposite directions of passage corresponding to the passage of one or the other of the two reports associated with the stock in which it was previously engaged.

Conformément à l'invention, la boîte de vitesses représentée aux figures 1 à 5 comporte un dispositif de freinage de pignons comportant des moyens provoquant une partie du déplacement axial du premier coulisseau 30, lors du mouvement de sélection du rapport de marche arrière non synchronisé, de façon à entraîner le synchroniseur du cinquième rapport de marche avant préalablement au passage du rapport de marche arrière.In accordance with the invention, the gearbox shown in FIGS. 1 to 5 comprises a pinion braking device comprising means causing part of the axial displacement of the first slider 30, during the movement for selecting the non-synchronized reverse gear ratio, so as to drive the synchronizer of the fifth forward gear prior to the passage of the reverse gear.

Ces moyens sont constitués par une rampe inclinée 56 formée sur la première partie 54, soli­ daire du premier coulisseau 30, de la crosse en deux parties associée à l'axe de passage supérieur 12. La rampe 56 est orientée et dimensionnée de façon que, lorsque les deux parties 42 et 54 de la crosse sont en butée l'une contre l'autre, la distance moyenne "d" séparant la rampe 56 de l'élément d'entraînement 42 soit inférieure à la largeur axiale "1" du doigt de commande 20.These means consist of an inclined ramp 56 formed on the first part 54, soli Daire of the first slide 30, of the butt in two parts associated with the axis of upper passage 12. The ramp 56 is oriented and dimensioned so that, when the two parts 42 and 54 of the butt are in abutment one against the other, the average distance "d" separating the ramp 56 from the drive element 42 is less than the axial width "1" of the control finger 20.

Les deux coulisseaux 30 et 34, et donc les deux parties 42 et 54 de la crosse, sont sollicités élastiquement, dans une direction correspondant au rapprochement des deux parties de la crosse et à la coopération des surfaces de butée en vis-à-vis 50 et 52, au moyen d'un ressort de compression 58. Le res­sort de compression 58 est disposé entre un épaulement 60 de la fourchette 26 et un épaulement en vis-à-vis 62 du second coulisseau 34. Le ressort 58 est suscep­tible d'être comprimé axialement entre les épaulements 60 et 62, jusqu'à ce que ses spires deviennent jointi­ves, d'une course maximale "x" qui détermine le débat­tement relatif maximal entre le premier coulisseau 30 et le second coulisseau 34 et donc l'écartement maxi­mal possible entre l'élément d'entraînement 42 et la première partie 54 de la crosse. En variante, ce débattement et cet écartement maximal sont procurés par mise en contact de faces en vis-à-vis de parties extrêmes respectives des coulisseaux 30 et 34, les spires du ressort 58 n'étant alors plus jointives.The two slides 30 and 34, and therefore the two parts 42 and 54 of the stick, are resiliently biased, in a direction corresponding to the bringing together of the two parts of the stick and to the cooperation of the abutment surfaces facing each other 50 and 52, by means of a compression spring 58. The compression spring 58 is disposed between a shoulder 60 of the fork 26 and a shoulder facing 62 of the second slide 34. The spring 58 is capable of be compressed axially between the shoulders 60 and 62, until its turns become contiguous, with a maximum stroke "x" which determines the maximum relative travel between the first slide 30 and the second slide 34 and therefore the maximum spacing possible between the drive element 42 and the first part 54 of the stick. As a variant, this clearance and this maximum spacing are provided by bringing the faces into contact with respective end portions of the slides 30 and 34, the turns of the spring 58 then no longer being contiguous.

On décrira maintenant le mode de fonctionne­ment du dispositif de freinage selon l'invention en partant de la position de repos du doigt de commande 20 représentée aux figures 1, 2, 4 et 5a.The mode of operation of the braking device according to the invention will now be described starting from the rest position of the control finger 20 shown in FIGS. 1, 2, 4 and 5a.

A partir de la position de point mort du doigt de commande 20, un mouvement de sélection vers le haut de ce dernier provoque son engagement entre les deux parties 42 et 54. Lors de cet engagement, la surface périphérique du doigt de commande 20 coopère avec la rampe 56 de façon à provoquer un déplacement axial, vers la droite, de la première partie de la crosse 54. Ce déplacement axial de la partie 54 provoque un déplacement axial de même valuer du premier coulisseau 30 dans le sens correspondant au passage du cinquième rapport de marche avant.From the neutral position of the control finger 20, a selection movement towards the top of the latter causes its engagement between the two parts 42 and 54. During this engagement, the peripheral surface of the control finger 20 cooperates with the ramp 56 so as to cause an axial displacement, to the right, of the first part of the butt 54. This axial displacement of the part 54 causes an axial displacement of the same value of the first slide 30 in the direction corresponding to the passage of the fifth forward gear.

Conformément à l'invention, le tarage élastique du billage de point mort 36 du second coulisseau 34 possède une valeur suffisamment élevée de manière à immobiliser axialement le second coulis­seau 34 par rapport au carter 10 lorsque le doigt de commande 20 coopère avec la rampe 56, et à permettre à l'élément d'entraînement 42 d'encaisser l'effort de réaction à la poussée P exercée sur le doigt de commande 20.In accordance with the invention, the elastic calibration of the neutral point billing 36 of the second slide 34 has a sufficiently high value so as to immobilize the second slide 34 axially relative to the casing 10 when the control finger 20 cooperates with the ramp 56, and allowing the drive element 42 to absorb the force of reaction to the thrust P exerted on the control finger 20.

A la fin de son mouvement de sélection, le doigt de commande 20 est totalement engagé à l'inté­rieur de la crosse en deux parties dont il a provoqué un écartement axial d'une valeur x égale à la valeur maximale de débattement relatif possible entre les deux coulisseaux 30 et 34, le ressort 58 étant alors comprimé de cette valeur x et ses spires étant jointi­ves.At the end of its selection movement, the control finger 20 is fully engaged inside the stick in two parts of which it has caused an axial spacing of a value x equal to the maximum possible value of relative travel between the two sliders 30 and 34, the spring 58 then being compressed by this value x and its turns being contiguous.

Lors du mouvement de sélection, le déplace­ment vers la droite du premier coulisseau 30, d'une course égale à une partie du déplacement nécessaire au passage complet du cinquième rapport de marche avant, a pour effet de provoquer un entraînement du synchro­niseur au moyen de la fourchette 26.During the selection movement, the movement to the right of the first slide 30, of a stroke equal to part of the movement necessary for the complete passage of the fifth forward gear, has the effect of causing the synchronizer to be driven by means of the fork 26.

Le passage du rapport de marche arrière s'effectue, après le mouvement de sélection qui vient d'être décrit, en provoquant un déplacement axial du second coulisseau 34 vers la gauche, au moyen du doigt de commande 20. En partant de la position représentée aux figures 3 et 5b, dans laquelle les surfaces en vis-à-vis 50 et 52 sont désormais écartées l'une de l'autre, un actionnement du doigt de commande par le levier de changement de vitesses vers la gauche a pour effet de provoquer l'entraînement du second coulisseau 34. Le déplacement du second coulisseau 34, à l'encon­tre de l'effort élastique exercé par le dispositif de billage 36 provoque, par l'intermédiaire du ressort 58 dont les spires sont jointives, ou en variante, par l'intermédiaire des susdites faces en vis-à-vis, l'en­traînement de la fourchette 26 et ainsi du premier coulisseau 30 par rapport au carter 10 de la boîte de vitesses. Le déplacement vers la gauche du second coulisseau 30, c'est-à-dire dans le sens opposé au sens de passage du cinquième rapport de marche avant, provoque la rotation d'une fourchette 64 de passage de la marche arrière montée pivotante autour d'un axe 66 du carter 10 et dont une extrémité 68 est reçue dans une encoche correspondante 70 du premier coulisseau 30. Le déplacement de celui-ci provoque en outre le débrayage du synchroniseur du cinquième rapport, ce qui rend libre l'engagement des dentures de marche arrière.The reverse gear is shifted after the selection movement which comes to be described, by causing an axial displacement of the second slide 34 to the left, by means of the control finger 20. Starting from the position shown in FIGS. 3 and 5b, in which the facing surfaces 50 and 52 are now separated from each other, an actuation of the control finger by the gear shift lever to the left has the effect of causing the drive of the second slide 34. The displacement of the second slide 34, at the 'against the elastic force exerted by the billing device 36 causes, via the spring 58 whose turns are contiguous, or alternatively, via the above faces opposite, the drive of the fork 26 and thus of the first slide 30 relative to the casing 10 of the gearbox. The displacement to the left of the second slide 30, that is to say in the direction opposite to the direction of passage of the fifth forward gear, causes the rotation of a fork 64 for shifting the reverse gear pivotally mounted around 'an axis 66 of the casing 10 and one end 68 of which is received in a corresponding notch 70 of the first slide 30. The displacement of the latter also causes the synchronizer of the fifth gear to disengage, which makes the engagement of the teeth free reverse gear.

En partant de la position représentée aux figures 3 et 5b, le passage du cinquième rapport de marche avant s'effectue, de manière classique, en déplaçant le doigt de commande 20 vers la droite de manière à entraîner directement le premier coulisseau 30 dans la même direction et ainsi la fourchette de passage 26. L'action du synchroniseur s'effectuant dès le mouvement de sélection, la course du coulisseau 30, et par suite du levier de changement de vitesses, pour le passage du cinquième rapport, est plus courte que dans les dispositifs usuels de commande où le synchro­niseur agit lors du déplacement du coulisseau.Starting from the position shown in Figures 3 and 5b, the passage of the fifth forward gear is carried out, in a conventional manner, by moving the control finger 20 to the right so as to directly drive the first slide 30 in the same direction and thus the shift fork 26. The action of the synchronizer being effected from the selection movement, the stroke of the slide 30, and consequently the gear shift lever, to the passage of the fifth gear is shorter than in the usual control devices where the synchronizer acts during the displacement of the slide.

La sélection et le passage des quatre pre­miers rapports de marche avant s'effectue d'une ma­nière classique qui ne sera pas décrite ici.The selection and shifting of the first four forward gears is carried out in a conventional manner which will not be described here.

On décrira maintenant un second mode de réalisation du dispositif selon l'invention appliqué à une boîte de vitesses à quatre couloirs de passage. Dans cette description, les éléments identiques ou équivalents à ceux du premier mode de réalisation sont désignés par les mêmes chiffres de référence augmentés de 100.We will now describe a second embodiment of the device according to the invention applied to a gearbox with four passage lanes. In this description, the elements identical or equivalent to those of the first embodiment are designated by the same reference numbers increased by 100.

Le dispositif de commande la boîte de com­mande représenté aux figures 6 à 7c permet la commande du changement de rapport d'une boîte de vitesses à cinq rapports de marche avant et à un rapport de marche arrière. Les éléments mobiles usuels non représentés, pour l'engagement alternatif d'engrenages correspondant aux divers rapports, peuvent être dépla­cés à l'aide de quatre crosses coulissantes respecti­vement solidaires de quatre coulisseaux parallèles qui sont agencés dans le carter de la boîte de vitesses. Les deux crosses centrales 122 et 124 sont associées à deux coulisseaux de façon à permettre, d'une manière classique, le passage des quatre premiers rapports de marche avant.The control device the control box shown in Figures 6 to 7c allows the control of the gear change of a gearbox with five forward gears and one reverse gear. The usual movable elements not shown, for the alternative engagement of gears corresponding to the various ratios, can be moved using four sliding sticks respectively integral with four parallel slides which are arranged in the casing of the gearbox. The two central sticks 122 and 124 are associated with two slides so as to allow, in a conventional manner, the passage of the first four forward gears.

La crosse latérale de droite, solidaire d'un premier coulisseau 130 permet la sélection et le passage du cinquième rapport de marche avant. A cet effet elle comporte une branche verticale 154 avec laquelle est susceptible de coopérer un premier doigt de commande 120 du cinquième rapport de marche avant synchronisé. Le doigt de commande 120 est immobilisé en rotation et en translation par rapport à un arbre de commande 70 de la sélection et du passage des vitesses, monté coulissant et rotatif dans le carter de la boîte de vitesses. Un second doigt de commande 72 est monté sur l'arbre de commande 70 par rapport auquel il est également immobilisé en translation et en rotation. L'extrémité inférieure 74 du second doigt de commande 72 est susceptible de coopérer avec un élément d'entraînement 142 formé par une branche ver­ticale d'un second coulisseau 134 auquel est relié le pignon du rapport de marche arrière non synchronisé.The right side stock, integral with a first slide 130 allows the selection and the passage of the fifth forward gear. To this end, it comprises a vertical branch 154 with which a first control finger 120 of the fifth synchronized forward gear is capable of cooperating. The control finger 120 is immobilized in rotation and in translation relative to a control shaft 70 for the selection and shifting of gears, mounted sliding and rotatable in the casing of the gearbox. A second control finger 72 is mounted on the control shaft 70 relative to which it is also immobilized in translation and in rotation. The lower end 74 of the second control finger 72 is capable of cooperating with a drive element 142 formed by a vertical branch of a second slide 134 to which the gear of the non-synchronized reverse gear is connected.

Le passage du cinquième rapport de marche avant synchronisé s'effectue en faisant coulisser le premier coulisseau 130 parallèlement à sa direction de passage, c'est-à-dire selon une direction perpendicu­laire à la direction de sélection qui est parallèle à l'axe de commande 70. Le passage du rapport de marche arrière s'effectue en provoquant un déplacement du second coulisseau 134 parallèlement à la direction de passage du cinquième rapport de marche avant mais dans le sens opposé au sens de passage de ce dernier rapport.The passage of the fifth synchronized forward gear is effected by sliding the first slider 130 parallel to its direction of passage, that is to say in a direction perpendicular to the selection direction which is parallel to the axis of command 70. The shift from the reverse gear is effected by causing the second slide 134 to move parallel to the direction of passage of the fifth forward gear but in the opposite direction to the direction of shift of the latter gear.

Conformément à l'invention, la partie de crosse 154 du premier coulisseau 130 comporte une rampe 156 avec laquelle coopère le premier doigt de commande 120 du cinquième rapport de marche avant synchronisé lorsque qu'il est déplacé, dans la direction de sélection, vers la droite en considérant les figures, jusqu'à ce qu'il soit complètement engagé à l'intérieur de la crosse du premier coulisseau 130 et tel que représenté à la figure 7c. Etant donné que le second doigt de commande 72 est lié en translation au premier doigt de commande 120, le déplacement de ce dernier vers la droite provoque un déplacement du second doigt de commande 72 de façon que ce dernier soit amené simultanément en vis-à-vis de l'élément d'entraînement 142 du second coulisseau 134 comme on peut le constater aux figures 7b et 7c.According to the invention, the butt portion 154 of the first slide 130 comprises a ramp 156 with which the first control finger 120 of the fifth synchronized forward gear cooperates when it is moved, in the selection direction, towards the right considering the figures, until it is fully engaged inside the butt of the first slide 130 and as shown in Figure 7c. Since the second control finger 72 is linked in translation to the first control finger 120, the movement of the latter to the right causes a displacement of the second control finger 72 so that the latter is brought simultaneously opposite the drive element 142 of the second slide 134 as can be seen in Figures 7b and 7c.

L'engagement du premier doigt de commande 120 à l'intérieur de la crosse du premier coulisseau 130 provoque un déplacement, vers le haut en considé­rant les figures 7a à 7c, de la partie de crosse 154 et donc du premier coulisseau 130 d'une course "x" dont la valeur est déterminée par le profil et l'orientation de la rampe 156.The engagement of the first control finger 120 inside the stock of the first slide 130 causes an upward movement, considering FIGS. 7a to 7c, of the stock portion 154 and therefore of the first slide 130 of a stroke "x" whose value is determined by the profile and orientation of the ramp 156.

Le déplacement du premier coulisseau 130 d'une course "x" égale à une partie de son déplacement axial dans le sens du passage de la cinquième vitesse a pour effet de provoquer l'entraînement du synchroni­seur équipant le cinquième rapport de marche avant et donc de provoquer un freinage du pignon d'entrée de la boîte de vitesses.The displacement of the first slide 130 of a stroke "x" equal to part of its axial displacement in the direction of passage of the fifth speed has the effect of causing the synchronizer fitted to the fifth forward gear and therefore to cause the gearbox input gear to brake.

Le passage du rapport de marche arrière, en partant de la position illustrée à la figure 7c, s'effectue au moyen du levier de changement de vites­ses qui provoque une rotation de l'arbre de commande 70 de manière à déplacer l'extrémité libre 74 du second doigt de commande 72, vers le bas en considé­rant la figure 7c, pour entraîner l'élément d'entraî­nement 142. Afin d'assurer le retour à sa position de point mort du premier coulisseau 130, la crosse équipant ce dernier comporte une saillie 76. La saillie 76 s'étend verticalement et est disposée en vis-à-vis de la rampe 156. Le premier doigt de comman­de 120 coopère avec la saillie 76, lors de la fin de l'opération de passage du rapport de marche arrière non synchronisé, de façon à ramener le premier coulis­seau 130 dans sa position de point mort représentée en trait mixte à la figure 7c.The shift from the reverse gear, starting from the position illustrated in FIG. 7c, is effected by means of the gear change lever which causes the control shaft 70 to rotate so as to move the free end 74 of the second control finger 72, downwards considering FIG. 7c, to drive the drive element 142. In order to ensure the return to its neutral position of the first slide 130, the stock fitted to the latter comprises a projection 76. The projection 76 extends vertically and is arranged opposite the ramp 156. The first control finger 120 cooperates with the projection 76, at the end of the shifting operation. rear non-synchronized, so as to return the first slide 130 to its neutral position shown in dashed line in Figure 7c.

Grâce à l'invention qui vient d'être décri­te, et selon ses deux modes de réalisation, on a réalisé un dispositif de freinage de pignons qui utilise un engagement et un entraînement partiel du synchroniseur du cinquième rapport de marche avant qui est provoqué par le mouvement de sélection du rapport de marche arrière non synchronisé. Le dispositif pro­posé, simple et fiable, en particulier grâce à la coo­pération directe du doigt avec une rampe agencée sur le coulisseau du rapport le plus long, agit effica­cement lors de chaque opération de passage de la marche arrière et évite les craquements indésirables de la pignonerie de la boîte de vitesses, notamment grâce au débrayage positif du synchroniseur en fin de course correspondant à ce passage.Thanks to the invention which has just been described, and according to its two embodiments, a pinion braking device has been produced which uses engagement and partial drive of the synchronizer of the fifth forward gear which is caused by the non-synchronized reverse gear selection movement. The proposed device, simple and reliable, in particular thanks to the direct cooperation of the finger with a ramp arranged on the slide of the longest gear, acts effectively during each operation of shifting from reverse and avoids the undesirable creaking of the gable of the gearbox, in particular thanks to the positive disengagement of the synchronizer at the end of the stroke corresponding to this passage.

Claims (8)

1. Dispositif de freinage de pignons d'une boîte de vitesses de véhicule automobile comportant au moins un rapport (5ème) équipé d'un synchroniseur à friction actionné par un premier coulisseau (30, 130) dont le déplacement axial, dans le sens du passage, est commandé par un doigt (20, 120) préalablement engagé dans une crosse de commande (42-54-142-154) solidaire du coulisseau, depuis une position de point mort, par un mouvement de sélection selon une direc­tion perpendiculaire à l'axe de déplacement du coulis­seau, et un rapport non synchronisé (AR) dont le passage est commandé par déplacement axial d'un second coulisseau (34, 134), parallèlement au premier coulis­seau et dans le sens opposé au sens de passage de ce dernier, au moyen d'un doigt (20, 72) préalablement amené en vis-à-vis d'un élément d'entraînement (42, 142) solidaire du second coulisseau, par un mouvement de sélection de même sens et d'amplitude égale ou supérieure à ceux du mouvement de sélection du rapport synchronisé, le dispositif comportant également des moyens provoquant une partie (x) dudit déplacement axial du premier coulisseau, lors du mouvement de sélection du rapport non synchronisé, de façon à entraîner le synchroniseur préalablement au passage du rapport non synchronisé, caractérisé en ce que lesdits moyens comportent une rampe (56, 156), formée sur une partie (54, 154) de la crosse de commande du premier coulisseau, avec laquelle coopère le doigt de commande (20, 120) du rapport synchronisé lorsque le doigt de commande du rapport non synchronisé est amené en vis-à-vis de l'élément d'entraînement.1. Gear braking device of a motor vehicle gearbox comprising at least one gear (5th) equipped with a friction synchronizer actuated by a first slide (30, 130) whose axial displacement, in the direction of passage, is controlled by a finger (20, 120) previously engaged in a control stick (42-54-142-154) secured to the slide, from a neutral position, by a selection movement in a direction perpendicular to the axis of displacement of the slide, and an unsynchronized ratio (AR) whose passage is controlled by axial displacement of a second slide (34, 134), parallel to the first slide and in the direction opposite to the direction of passage of the latter , by means of a finger (20, 72) previously brought opposite a drive element (42, 142) integral with the second slide, by a selection movement of the same direction and of equal amplitude or higher than those of the synchronous gear selection movement sé, the device also comprising means causing part (x) of said axial displacement of the first slide, during the movement of selection of the non-synchronized report, so as to drive the synchronizer prior to the passage of the non-synchronized report, characterized in that said means comprise a ramp (56, 156), formed on a part (54, 154) of the control stick of the first slide, with which the control finger (20, 120) of the synchronized gear cooperates when the gear control finger not synchronized is brought opposite the drive element. 2. Dispositif de freinage de pignons selon la revendication 1 caractérisé en ce que chacun des deux coulisseaux est équipé d'un dispositif de billage de point mort et en ce que celui (36) associé au second coulisseau est taré élastiquement de manière à immobiliser axialement ce dernier par rapport au carter (10) de la boîte de vitesses lorsque le doigt de commande du rapport synchronisé coopère avec ladite rampe (56).2. pinion braking device according to claim 1 characterized in that each of two sliders is equipped with a neutral point billing device and in that that (36) associated with the second slider is calibrated elastically so as to immobilize the latter axially relative to the casing (10) of the gearbox when the finger synchronized report control system cooperates with said ramp (56). 3. Dispositif de freinage de pignons selon l'une des revendications 1 ou 2 caractérisé en ce que les deux coulisseaux (30, 34) sont coaxiaux et mobiles axialement l'un par rapport à l'autre d'une course maximale sensiblement égale à ladite partie (x) du déplacement axial du premier coulisseau, en ce que ladite crosse comprend une première partie (54) soli­daire du premier coulisseau (30) et sur laquelle est formée ladite rampe (56), et une seconde partie (42) solidaire du second coulisseau (34), disposée en vis-à-vis de la première partie, et qui constitue ledit élément d'entraînement, et en ce que les doigts de commande des rapports synchronisé et non synchro­nisé sont un doigt unique (20).3. pinion braking device according to one of claims 1 or 2 characterized in that the two slides (30, 34) are coaxial and axially movable relative to each other with a maximum stroke substantially equal to said part (x) of the axial displacement of the first slide, in that said stock comprises a first part (54) secured to the first slide (30) and on which said ramp (56) is formed, and a second part (42) secured of the second slide (34), disposed opposite the first part, and which constitutes said drive element, and in that the fingers for controlling the synchronized and unsynchronized reports are a single finger (20). 4. Dispositif de freinage de pignons selon la revendication 3 caractérisé en ce qu'il comporte un ressort de rappel (58) qui sollicite élastiquement les deux parties (42, 54) de la crosse en butée l'une contre l'autre.4. pinion braking device according to claim 3 characterized in that it comprises a return spring (58) which resiliently biases the two parts (42, 54) of the stick abutting one against the other. 5. Dispositif de freinage de pignons selon la revendication 4 caractérisé en ce que le ressort de rappel (58) est un ressort de compression coaxial aux deux coulisseaux et dont la course maximale de com­pression à spires jointives est égale à ladite course maximale de débattement relatif des deux coulisseaux.5. sprocket braking device according to claim 4 characterized in that the return spring (58) is a compression spring coaxial with the two sliders and whose maximum compression stroke with contiguous turns is equal to said maximum stroke of relative movement of the two slides. 6. Dispositif de freinage de pignons selon l'une des revendications 3 ou 4, caractérisé en ce que la course maximale entre les deux couliseaux (30, 34) est obtenue par mise en contact de deux faces en vis-­à-vis de parties extrêmes respectives de ces deux coulisseaux.6. pinion braking device according to one of claims 3 or 4, characterized in that the maximum travel between the two sliders (30, 34) is obtained by bringing two faces into contact with respective end portions of these two sliders. 7. Dispositif de freinage de pignons selon l'une des revendications 1 ou 2, caractérisé en ce que le doigt de commande (120) du rapport synchronisé et le doigt de commande (72) du rapport non synchronisé sont deux doigts distincts liés en translation et en rotation à un arbre de commande (70) monté coulissant et rotatif dans le carter de la boîte de vitesses, et en ce que ladite crosse comporte une saillie (76), disposée en vis-à-vis de ladite rampe (156), avec laquelle coopère le doigt de commande (120) du rapport synchronisé, en fin de passage du rapport non synchro­nisé, de façon à ramener le premier coulisseau (130) dans sa position de point mort.7. pinion braking device according to one of claims 1 or 2, characterized in that the control finger (120) of the synchronized gear and the control finger (72) of the non-synchronized gear are two separate fingers linked in translation and in rotation to a control shaft (70) slidably and rotatably mounted in the gearbox casing, and in that said stock has a projection (76), disposed opposite said ramp (156) , with which the control finger (120) of the synchronized gear cooperates, at the end of passage of the non-synchronized gear, so as to bring the first slide (130) back into its neutral position. 8. Dispositif de freinage de pignons selon l'une quelconque des revendications précédentes carac­térisé en ce que le rapport non synchronisé est la marche arrière et en ce que le rapport synchronisé est le rapport de marche avant de rang le plus élevé.8. pinion braking device according to any one of the preceding claims, characterized in that the non-synchronized ratio is reverse and in that the synchronized ratio is the highest-ranking forward ratio.
EP88401455A 1987-07-20 1988-06-13 Gear pinion brake device of a motor vehicle gearbox Expired - Lifetime EP0300843B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8710239 1987-07-20
FR8710239A FR2618510B1 (en) 1987-07-20 1987-07-20 DEVICE BRAKE DEVICE OF A MOTOR VEHICLE GEARBOX

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EP0300843A1 true EP0300843A1 (en) 1989-01-25
EP0300843B1 EP0300843B1 (en) 1990-06-13

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EP (1) EP0300843B1 (en)
DE (1) DE3860228D1 (en)
FR (1) FR2618510B1 (en)

Cited By (19)

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Publication number Priority date Publication date Assignee Title
EP0459859A1 (en) * 1990-05-30 1991-12-04 Automobiles Peugeot Device for braking gears in a gearbox of a motor vehicle
FR2673254A1 (en) * 1991-02-25 1992-08-28 Peugeot DEVICE FOR CONTROLLING A GEARBOX.
EP0708277A1 (en) * 1994-10-18 1996-04-24 Société Anonyme dite: REGIE NATIONALE DES USINES RENAULT Device and method for controlling a gearbox
EP0770802A2 (en) * 1995-10-25 1997-05-02 Ford-Werke Aktiengesellschaft Shift device for automotive vehicle transmission with means for braking the input shaft during selection of reverse gear
EP0699854A3 (en) * 1994-08-31 1997-12-17 Suzuki Motor Corporation Reverse gear squeal-preventing device
EP0866239A3 (en) * 1997-03-18 1999-07-07 New Venture Gear, Inc. Multi-speed manual transmission with reverse brake
WO2003062678A1 (en) * 2002-01-25 2003-07-31 Eaton Coproration Gearshift apparatus for multi-gear transmissions
EP1510733A1 (en) * 2003-08-29 2005-03-02 Peugeot Citroen Automobiles S.A. Internal control device for a gearbox
EP2028396A2 (en) 2007-08-09 2009-02-25 Mitsubishi Jidosha Kogyo Kabushiki Kaisha Transmission
EP2000707A3 (en) * 2007-06-07 2009-11-25 Mitsubishi Jidosha Kogyo Kabushiki Kaisha Transmission
EP2053282A3 (en) * 2007-10-25 2010-04-28 Toyota Jidosha Kabusiki Kaisha Gear noise prevention system for manual transmission
EP2107279A3 (en) * 2008-04-01 2010-04-28 Toyota Jidosha Kabusiki Kaisha Gear whine prevention device for manual transmission
EP2090811A3 (en) * 2008-02-12 2010-05-26 Toyota Jidosha Kabushiki Kaisha Gear noise preventing device for manual transmission
EP2199647A1 (en) * 2008-12-19 2010-06-23 Peugeot Citroen Automobiles SA Manual gearbox with a synchromesh mechanism during a reverse shift select operation
FR2959791A1 (en) * 2010-05-06 2011-11-11 Peugeot Citroen Automobiles Sa System for controlling gearbox of motor vehicle, has brake assembly with stop component that is in free state with respect to interlocking key when movement of spindle wharve is authorized
FR3023345A1 (en) * 2014-07-01 2016-01-08 Peugeot Citroen Automobiles Sa CONTROL SYSTEM FOR A VEHICLE GEARBOX
WO2016071588A1 (en) * 2014-11-07 2016-05-12 Renault S.A.S Device for braking and internal control of reversing in a gearbox
CN106438994A (en) * 2015-08-06 2017-02-22 贺尔碧格汽车舒适系统有限责任公司 Shifting servo
CN115059758A (en) * 2022-06-27 2022-09-16 江西福格新能源传动技术有限公司 Transmission shaft locking device for new energy automobile gearbox and implementation method thereof

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DE102009025452A1 (en) 2009-06-10 2010-12-16 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Switching device for multi-stage standard transmission i.e. manual transmission, of motor vehicle, has hand lever adjusted in gear shifting gate such that engagement of gears is associated with switching lane in selection position

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Cited By (31)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0459859A1 (en) * 1990-05-30 1991-12-04 Automobiles Peugeot Device for braking gears in a gearbox of a motor vehicle
FR2662775A1 (en) * 1990-05-30 1991-12-06 Peugeot GEAR BRAKING DEVICE FOR A MOTOR VEHICLE GEARBOX.
FR2673254A1 (en) * 1991-02-25 1992-08-28 Peugeot DEVICE FOR CONTROLLING A GEARBOX.
EP0501845A1 (en) * 1991-02-25 1992-09-02 Automobiles Peugeot Control device for a gearbox
EP0699854A3 (en) * 1994-08-31 1997-12-17 Suzuki Motor Corporation Reverse gear squeal-preventing device
EP0708277A1 (en) * 1994-10-18 1996-04-24 Société Anonyme dite: REGIE NATIONALE DES USINES RENAULT Device and method for controlling a gearbox
EP0770802A2 (en) * 1995-10-25 1997-05-02 Ford-Werke Aktiengesellschaft Shift device for automotive vehicle transmission with means for braking the input shaft during selection of reverse gear
EP0770802A3 (en) * 1995-10-25 1999-02-03 Ford Global Technologies, Inc. Shift device for automotive vehicle transmission with means for braking the input shaft during selection of reverse gear
EP0866239A3 (en) * 1997-03-18 1999-07-07 New Venture Gear, Inc. Multi-speed manual transmission with reverse brake
WO2003062678A1 (en) * 2002-01-25 2003-07-31 Eaton Coproration Gearshift apparatus for multi-gear transmissions
EP1510733A1 (en) * 2003-08-29 2005-03-02 Peugeot Citroen Automobiles S.A. Internal control device for a gearbox
FR2859262A1 (en) * 2003-08-29 2005-03-04 Peugeot Citroen Automobiles Sa INTERNAL CONTROL SYSTEM FOR GEARBOX
EP2000707A3 (en) * 2007-06-07 2009-11-25 Mitsubishi Jidosha Kogyo Kabushiki Kaisha Transmission
EP2028396A3 (en) * 2007-08-09 2009-12-02 Mitsubishi Jidosha Kogyo Kabushiki Kaisha Transmission
CN101363537B (en) * 2007-08-09 2012-11-28 三菱自动车工业株式会社 Transmission
EP2028396A2 (en) 2007-08-09 2009-02-25 Mitsubishi Jidosha Kogyo Kabushiki Kaisha Transmission
EP2053282A3 (en) * 2007-10-25 2010-04-28 Toyota Jidosha Kabusiki Kaisha Gear noise prevention system for manual transmission
CN101418855B (en) * 2007-10-25 2013-04-24 丰田自动车株式会社 Gear noise preventing system for manual transmission
EP2090811A3 (en) * 2008-02-12 2010-05-26 Toyota Jidosha Kabushiki Kaisha Gear noise preventing device for manual transmission
CN101509552B (en) * 2008-02-12 2013-01-02 丰田自动车株式会社 Gear noise preventing device for manual transmission
EP2107279A3 (en) * 2008-04-01 2010-04-28 Toyota Jidosha Kabusiki Kaisha Gear whine prevention device for manual transmission
EP2199647A1 (en) * 2008-12-19 2010-06-23 Peugeot Citroen Automobiles SA Manual gearbox with a synchromesh mechanism during a reverse shift select operation
FR2940386A1 (en) * 2008-12-19 2010-06-25 Peugeot Citroen Automobiles Sa MANUAL GEARBOX WITH TRANSLATION PASSAGE AND ROTATION SELECTION COMPRISING A REVERSE BRAKE USING A FRONT MOTION SYNCHRONIZER
FR2959791A1 (en) * 2010-05-06 2011-11-11 Peugeot Citroen Automobiles Sa System for controlling gearbox of motor vehicle, has brake assembly with stop component that is in free state with respect to interlocking key when movement of spindle wharve is authorized
FR3023345A1 (en) * 2014-07-01 2016-01-08 Peugeot Citroen Automobiles Sa CONTROL SYSTEM FOR A VEHICLE GEARBOX
WO2016071588A1 (en) * 2014-11-07 2016-05-12 Renault S.A.S Device for braking and internal control of reversing in a gearbox
FR3028301A1 (en) * 2014-11-07 2016-05-13 Renault Sa BRAKING DEVICE AND INTERNAL REVERSE CONTROL FOR GEARBOX
RU2676193C2 (en) * 2014-11-07 2018-12-26 Рено С.А.С. Device of reverse gear braking and internal drive of reverse gear for gearbox
CN106438994A (en) * 2015-08-06 2017-02-22 贺尔碧格汽车舒适系统有限责任公司 Shifting servo
CN115059758A (en) * 2022-06-27 2022-09-16 江西福格新能源传动技术有限公司 Transmission shaft locking device for new energy automobile gearbox and implementation method thereof
CN115059758B (en) * 2022-06-27 2023-10-13 江西福格新能源传动技术有限公司 Transmission shaft locking equipment for new energy automobile gearbox and implementation method thereof

Also Published As

Publication number Publication date
FR2618510B1 (en) 1989-12-08
EP0300843B1 (en) 1990-06-13
DE3860228D1 (en) 1990-07-19
FR2618510A1 (en) 1989-01-27

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